JP2016080117A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission capable of preventing generation of creep of an outer ring fitting face without spending a processing cost of an outer ring of a bearing.SOLUTION: An outer ring 45a of a bearing 45 rotatably supporting an inner disc 3 is fitted to the inner disc 3, and fitted to both of a side face of the outer ring 45a and an inner diameter face of an output gear 41, thus a fitting member 47 for making a transmission gear 41 and the outer ring 45a integrally rotatable, is disposed coaxially with the output gear 41 and the outer ring 45a, and relative rotation of the inner disc 3 rotating with the output gear 41 and the outer ring 45a can be suppressed. Accordingly, generation of creep of an outer ring fitting face of the inner disc 3 and an outer diameter face of the outer ring 45a can be prevented, and further it is unnecessary to form a radially-extended flange on the outer ring 45a as different from a conventional one, which reduces processing cost of the outer ring.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a toroidal continuously variable transmission that can be used for transmissions of automobiles and various industrial machines.

For example, a double-cavity toroidal continuously variable transmission used as an automobile transmission is configured as shown in FIGS. As shown in FIG. 3, an input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the input shaft 1. 3 is attached. An output gear (transmission gear) 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.
The input shaft 1 is rotationally driven by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate (loading cam) 7 located on the left side in FIG. It is like that. The output gear 4 is supported in the casing 50 via a partition wall 13 formed by coupling two members, so that the output gear 4 can rotate around the axis O of the input shaft 1 while the axis O. Directional displacement is prevented.

  The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 and rotatable about the axis O of the input shaft 1. Further, the input disc 2 on the left side in FIG. 3 is supported on the input shaft 1 via a ball spline 6, and the input disc 2 on the right side in FIG. 3 is splined to the input shaft 1. The disk 2 rotates with the input shaft 1. Further, there is power between the inner side surfaces (concave surface; also referred to as a traction surface) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surface; also referred to as a traction surface) 3a and 3a of the output side disks 3 and 3. A roller 11 (see FIG. 4) is rotatably held.

  A step portion 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 3, and the step portion 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step portion 2b. At the same time, the back surface (right surface in FIG. 3) of the input side disk 2 is abutted against a loading nut 9 screwed into a screw portion formed on the outer peripheral surface of the input shaft 1. Thereby, the displacement of the input side disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and a pressing portion (preload) is applied to a contact portion between the peripheral surfaces 11a and 11a of the power rollers 11 and 11.

  4 is a cross-sectional view taken along line AA in FIG. As shown in FIG. 4, a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In FIG. 4, the input shaft 1 is not shown. Each trunnion 15, 15 has a pair of bent wall portions 20, 20 formed at both ends in the longitudinal direction (vertical direction in FIG. 4) of the support plate portion 16 so as to be bent toward the inner side surface of the support plate portion 16. have. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

  A circular hole 21 is formed in the central portion of the support plate portion 16, and the base end portion 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. Each power roller 11 is rotatably supported around the distal end portion 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15, and each power roller 11, 11 is connected to each input side disk. 2 and 2 and between the output side disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  The pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable and displaceable in the axial direction (vertical direction in FIG. 4) with respect to the pair of yokes 23A and 23B, respectively. The horizontal movement of the trunnions 15 and 15 is restricted by 23B. Each yoke 23A, 23B is formed in a rectangular shape by pressing or forging a metal such as steel. Four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B, and the pivot shafts 14 provided at both ends of the trunnion 15 swing through the radial needle bearings 30. It is supported freely. In addition, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left and right direction in FIG. 4). The inner peripheral surface of the locking hole 19 is a cylindrical surface, and is a spherical post. 64 and 68 are fitted inside. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical post 68 and the drive for supporting the same. The upper cylinder body 56 of the cylinder 31 is swingably supported.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying an excessive force to the member.

  Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing (thrust bearing) 24 that is a thrust rolling bearing is sequentially formed from the outer surface side of the power roller 11. A thrust needle bearing 25 is provided. Among these, the thrust ball bearing 24 supports the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of such thrust ball bearings 24 includes a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular retainer 27 that holds the rolling elements 26, 26 in a freely rolling manner, And an annular outer ring 28. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  The thrust needle bearing 25 is sandwiched between the inner surface of the support plate portion 16 of the trunnion 15 and the outer surface of the outer ring 28. Such a thrust needle bearing 25 supports the thrust load applied to each outer ring 28 from the power roller 11, while the power roller 11 and the outer ring 28 swing around the base end portion 23 a of each displacement shaft 23. Allow.

  Further, driving rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 4) of the trunnions 15 and 15, respectively, and a driving piston ( Hydraulic pistons) 33, 33 are fixed. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 56 and a lower cylinder body 57. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to the input side disks 2 and 2 via the pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is further transmitted to the output gear 4. It is taken out more.

When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced in directions opposite to each other. For example, the power roller 11 on the left side in FIG. 4 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure.
As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing (tilt) in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 slightly rotate around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

By the way, in the conventional toroidal-type continuously variable transmission, as described above, a hole provided in the partition wall 13 in order to support the output gear (transmission gear) 4 in the casing 50 via the partition wall 13. A bearing (outer ring thereof) is fitted into the inner ring, and the output gear 4 is rotatably supported by the inner ring of the bearing.
However, since the outer ring of this bearing is fitted into the partition wall 13 by being fitted into a hole provided in the partition wall 13, it is difficult to sufficiently secure the fixing strength of the bearing with respect to the partition wall 13.
For this reason, there exists a possibility that the outer ring | wheel of a bearing may rotate with respect to the inner wall surface of the hole of the partition wall 13, ie, an outer ring fitting surface. When the outer ring of the bearing rotates relative to the outer ring fitting surface, creep may occur on the outer ring fitting surface.

  In view of such circumstances, in the toroidal continuously variable transmission described in Patent Document 1, a flange extending in the radial direction of the torque input shaft is formed on the outer ring of the bearing, and the outer edge of the flange is connected to the toroidal continuously variable transmission. By directly fixing to the casing, the fixing strength of the outer ring is increased, and the occurrence of creep of the outer ring fitting surface is prevented.

JP-A-11-210773

  However, the toroidal-type continuously variable transmission described in Patent Document 1 has a problem in that a processing cost for the outer ring is increased because a flange extending in the radial direction of the torque input shaft is formed on the outer ring of the bearing.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a toroidal continuously variable transmission that can prevent the occurrence of creep on the outer ring fitting surface without incurring the processing cost of the outer ring of the bearing.

To achieve the above object, a toroidal-type continuously variable transmission according to the present invention is sandwiched between a pair of disks rotatably supported with the inner surfaces facing each other, and the pair of disks. In a toroidal continuously variable transmission comprising a power roller and a transmission gear for power transmission fitted to one of the disks,
An outer ring of a bearing that rotatably supports one of the disks is fitted into one of the disks,
By fitting both the side surface of the outer ring and the inner diameter surface of the transmission gear, a fitting member that allows the transmission gear and the outer ring to rotate integrally is provided coaxially with the transmission gear and the outer ring. It is characterized by being.

  In the present invention, the transmission gear and the outer ring can be rotated integrally by fitting the fitting member to both the side surface of the outer ring of the bearing fitted in one of the disks and the inner diameter surface of the transmission gear. Therefore, relative rotation between the inner disk and the outer ring rotating together with the transmission gear can be suppressed. Therefore, creep of the outer ring fitting surface of one disk and the outer diameter surface of the outer ring can be prevented, and unlike the conventional case, it is not necessary to form a radially extending flange on the outer ring, which increases the processing cost of this outer ring. There is no.

  According to the present invention, since the relative rotation between the disk and the outer ring can be suppressed, the occurrence of creep of the outer ring fitting surface of the disk and the outer diameter surface of the outer ring can be prevented, and unlike the conventional case, the flange extends in the radial direction to the outer ring. Since it is not necessary to form the outer ring, there is no cost for processing the outer ring.

1 is a side sectional view showing a main part of a toroidal continuously variable transmission according to an embodiment of the present invention. FIG. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission. It is sectional drawing which follows the AA line in FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a side sectional view showing a main part of a toroidal type continuously variable transmission according to an embodiment of the present invention, and FIG. 2 is an exploded perspective view thereof.
The toroidal type continuously variable transmission according to the present embodiment is the same as the conventional toroidal type continuously variable transmission shown in FIGS. 3 and 4 except for the main parts shown in FIGS. The illustration and description of the common part are omitted. In FIGS. 1 and 2, the same reference numerals are assigned to the same parts as those in the conventional toroidal continuously variable transmission, and the description thereof is omitted or simplified.

As shown in FIGS. 1 and 2, in the toroidal-type continuously variable transmission of the present embodiment, a pair of left and right inner disks 3, 3 constitute output side disks 3, 3.
A cylindrical portion 40 having a small diameter is provided coaxially and integrally with the output side disk 3 on the large end surface of the output side disk 3, and spline protrusions and spline grooves are formed on the outer diameter surface of the cylindrical portion 40. The spline part 40a which has these is formed.
The inner diameter of the cylindrical portion 40 is set to be larger than the inner diameter of the output-side disk 3, whereby a predetermined step surface 3 d is provided between the inner diameter surface of the cylindrical portion 40 and the inner diameter surface of the output-side disk 3. Yes. One side surface of an outer ring 45a of a bearing 45 described later is brought into contact with the step surface 3d.

An output gear (transmission gear) 41 for power transmission is provided coaxially with the output side disks 3 and 3 between the pair of left and right output side disks 3 and 3. The output gear 41 is provided between the outer cylinder part 42, the inner cylinder part 43 coaxially provided inside the outer cylinder part 42, and the outer cylinder part 42 and the inner cylinder part 43, and connects them. And a ring portion 44 to be configured.
The outer cylinder part 42 is shorter in the axial direction than the inner cylinder part 43, and a gear part 42 a is formed on the outer diameter surface of the outer cylinder part 42.
In addition, a spline portion 43 a composed of spline protrusions and spline grooves is formed on the inner diameter surface of the inner cylinder portion 43.

The spline portion 43a of the output gear 41 is spline-coupled to the spline portions 40a, 40a of the cylindrical portions 40, 40 of the pair of left and right output side disks 3, 3, so that the output gear 41 is connected to the output side disks 3, 3. It is mated. Thus, the output gear 41 and the output side disks 3 and 3 are synchronously rotated around the axis without slipping in the circumferential direction.
Further, a predetermined gap is provided in the axial direction between the cylindrical portions 40, 40, and a spline portion 47c of the fitting member 47 described later is arranged in this gap.

Further, an outer ring 45a of a bearing 45 that rotatably supports the output side disk 3 is fitted into the cylindrical portion 40 of the output side disk 3. That is, the outer diameter surface of the outer ring 45a is in close contact with the inner diameter surface of the cylindrical portion 40, and one side surface of the outer ring 45a is in contact with the step surface 3d.
The bearing 45 includes an outer ring 45a, an inner ring 45b, and a spherical rolling element 45c provided between the outer ring 45a and the inner ring 45b.

The inner ring 45 b of the bearing 45 is located inside the inner diameter surface of the output side disk 3, and the inner ring 45 b is fitted into the input shaft 1 inserted through the inner diameter side of the output side disks 3 and 3. As a result, the output side disk 3 is rotatably supported by the input shaft 1 via the bearing 45.
A needle bearing 5 is provided between the inner diameter surface on the small end face side of the output side disk 3 and the input shaft 1. The output side disk 3 is also rotatably supported by the input shaft 1 via the needle bearing 5.

Further, on the other side surface of the outer ring 45a, convex portions 46a and 46a projecting along the axial direction are formed at two locations in the circumferential direction of the outer ring 45a so as to face each other in the radial direction. The convex portion 46a is formed in a substantially rectangular plate shape, and its outer surface and inner surface are substantially flush with the outer diameter surface and inner diameter surface of the outer ring 45a.
Further, between the output side disks 3 and 3, fitting members 47 and 47 are provided. The fitting member 47 engages both the side surface of the outer ring 45a and the inner diameter surface of the output gear 41 so that the output gear 41 and the outer ring 45a can be rotated integrally. An end portion of the cylindrical portion 47a has a ring portion 47b formed coaxially with the cylindrical portion 47a.
The cylindrical portion 47a has an outer diameter and an inner diameter equal to those of the outer ring 45a, and concave portions 46b and 46b that are fitted into the convex portions 46a and 46a in the concave and convex portions 46a and 46a are circumferentially arranged at the axial end edges of the cylindrical portion 47a. Are formed so as to face each other in the radial direction.
The ring portion 47b is formed to have a larger diameter than the cylindrical portion 47a, and a spline portion 47c made of a concavo-convex portion is formed on the outer peripheral portion thereof.

In the fitting member 47 having such a configuration, the cylindrical portion 47a is inserted inside the inner cylindrical portion 43 of the output gear 41 coaxially with the inner cylindrical portion 43 and the outer ring 45a, and the ring portion 47b is connected to the cylindrical portion 40, It is provided in the gap between 40. In this state, the spline portion 47c on the outer peripheral portion of the ring portion 47b is spline-coupled with the spline portion 43a formed on the inner diameter surface of the inner cylinder portion 43.
Further, the pair of left and right fitting members 47, 47 abut each other with their ring portions 47 b, 47 b back to back so that the axially central portion of the inner cylinder portion 43 is inside the inner cylinder portion 43 of the output gear 41. Are arranged.
Further, in a state where the fitting member 47 is inserted inside the inner cylinder portion 43 of the output gear 41 and the spline portion 47c is splined with the spline portion 43a, the convex portion 46a of the outer ring 45a and the concave portion of the fitting member 47. 46b is unevenly fitted. As a result, the output gear 41 and the outer ring 45 a are rotated together via the fitting member 47.

  In the toroidal type continuously variable transmission having such a configuration, it is fitted to both the side surface of the outer ring 45a of the bearing 45 fitted into the cylindrical portion 40 of the output side disk 3 and the inner diameter surface of the inner cylindrical portion 43 of the output gear 41. By fitting the joint member 47, that is, the convex portion 46 a provided on the side surface of the outer ring 45 a and the concave portion 46 b provided on the fitting member 47 are concave and convex, and the inner diameter of the inner cylinder portion 43 of the output gear 41 is obtained. When the spline portion 43a provided on the surface and the spline portion 47c provided on the fitting member 47 are engaged with each other by spline coupling, the fitting member 47 integrally rotates the output gear 41 and the outer ring 45a. Therefore, relative rotation between the cylindrical portion 40 of the output side disk 3 that rotates together with the output gear 41 and the outer ring 45a can be suppressed. Accordingly, creep of the outer ring fitting surface of the cylindrical portion 40 of the output side disk 3 (inner diameter surface of the cylindrical portion 40) and the outer diameter surface of the outer ring 45a can be prevented, and a flange extending radially in the outer ring 45a unlike the conventional case. Since it does not need to be formed, the processing cost of the outer ring 45a is not increased.

Further, since the fitting member 47 is not in contact with the output side disk 3, fretting wear caused by elastic deformation of the output side disk 3 can be prevented.
Further, the spline portion 43a of the output gear 41 is spline-coupled to the spline portion 40a of the cylindrical portion 40 of the output side disk 3, and the spline portion 47c of the fitting member 47 is spline-coupled to the spline portion 43a. There is no need to additionally process a portion that fits the fitting member 47, which is advantageous in terms of cost.

In the toroidal continuously variable transmission, the input / output relationship between the input side disk and the output side disk may be reversed. Therefore, the present invention can also be applied when the input side disk 2 and the output side disk 3 are interchanged.
Further, in the present embodiment, in order to fit the side surface of the outer ring 45a and the fitting member 47, the outer ring 45a is provided with a convex portion 46a, and the fitting member 47 is provided with a concave portion 46b that is unevenly fitted to the convex portion 46a. Although provided, the convex portions 46a and the concave portions 46b may be formed in reverse. Further, the means for fitting the side surface of the outer ring 45a and the fitting member 47 is not limited to the concave and convex fitting, and if the outer ring 45a and the fitting member 47 can rotate synchronously without slipping in the circumferential direction, Any fitting means may be used.
In addition to the double cavity type half toroidal continuously variable transmission, the present invention also includes a single cavity type half toroidal continuously variable transmission, a single cavity type full toroidal continuously variable transmission, a double cavity type full toroidal continuously variable transmission. It can also be applied to a transmission.

2 Input disk (disk)
3 Output side disk (disk)
11 Power roller 41 Output gear (transmission gear)
43a Spline part 45 Bearing 45a Outer ring 46a Convex part 46b Concave part 47 Fitting member 47c Spline part

Claims (1)

A pair of disks that are rotatably supported with their inner surfaces facing each other, a power roller sandwiched between the pair of disks, and a transmission gear for power transmission fitted to one of the disks In a toroidal type continuously variable transmission equipped with
An outer ring of a bearing that rotatably supports one of the disks is fitted into one of the disks,
By fitting both the side surface of the outer ring and the inner diameter surface of the transmission gear, a fitting member that allows the transmission gear and the outer ring to rotate integrally is provided coaxially with the transmission gear and the outer ring. Toroidal-type continuously variable transmission.

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